DE1294088B - Internal combustion engine set - Google Patents

Description

In the case of rotary piston internal combustion engines of the trochoid design, the housing has a two-arched inner jacket surface, prepares the application of the diesel process certain difficulties, primarily due to the fact that the the high compression required for the diesel process has a small swivel angle requires. This results in a relatively large construction volume for a given Chamber size, a large surface area of the working chamber at the moment of ignition elongated, sickle-shaped combustion chamber, which is incomplete with an injection nozzle can be detected, and a relatively weak eccentric shaft, since its diameter is limited by the pinion of the gear train keeping the piston in phase. Attempts have therefore already been made to build diesel machines with a larger pivot angle is and roughly corresponds to that of Otto rotary piston internal combustion engines, where the high compression ratio required for auto-ignition of the fuel was achieved by charging the internal combustion engines. The entire, The amount of air sucked in by the internal combustion engine is pre-compressed in the charger to such an extent that that the required in the subsequent compression in the internal combustion engine high compression ratio is achieved. This design has the disadvantage that the charger must be large and that when overflowing the pre-compressed Charge into the intake chamber of the internal combustion engine causes considerable throttle losses.

It is also an internal combustion engine set known, which consists of two inner-axis Rotary piston four-stroke internal combustion engines with two-arched inner lateral surface and triangular piston rotatably arranged on an eccentric shaft and a rotary piston displacement charger of the same design, the internal combustion engines in the area of their compression chamber have a loading opening that connects to the working spaces of the positive displacement loader a line are connected. Each internal combustion engine has its own Inlet port and the positive displacement charger are provided with two inlet ports, each be overridden by the pistons of the machine in question. The internal combustion engines and the positive displacement loader each suck in for themselves, and by appropriate arrangement of the loading openings is achieved that the compressed by the loader and into the internal combustion engine The charge pushed over together with the charge sucked in by the internal combustion engines is further compressed in the internal combustion engine. This can be done in the internal combustion engine a compression end pressure can be achieved, which is necessary for the implementation of a diesel process is sufficient without, as in other known supercharged internal combustion engines entire charge is pre-compressed in the displacement charger. The displacement loader can thus be dimensioned smaller.

The invention relates to an internal combustion engine set that works according to the diesel process, which consists of an internal-axis rotary piston four-stroke internal combustion engine with a two-arched inner surface and a triangular, rotatable on one Piston arranged on the eccentric shaft and a positive displacement charger coupled to this consists, the internal combustion engine having a loading opening in the area of its compression chamber which is connected to the working space of the positive displacement charger via a line is. The object of the invention consists in the structure of such an internal combustion engine set and above all to simplify the control of the positive displacement charger. This task is achieved according to the invention in that the positive displacement charger with the eccentric shaft the internal combustion engine is coupled in such a way that it is at 360 ° eccentric shaft rotation angle performs an intake and a compression stroke and its compression stroke at the same time begins with or shortly before the compression stroke of the internal combustion engine and that his Working space is only connected to the loading opening and this loading opening in the Area of the off-axis zone of the jacket is arranged. As the compression stroke of the rotary piston internal combustion engine over 270 °, that of the supercharger only over Extends 180 °, so is the simultaneous beginning of the compression strokes in both Machines the compression stroke of the positive displacement charger and thus the overflow process 90 ° eccentric shaft rotation angle before the end of the compression stroke of the internal combustion engine finished, d. h., The charge sucked in by the internal combustion engine itself and the During this 90 ° eccentric shaft rotation angle, the load pushed over by the loader compressed together in the internal combustion engine. At the end of the compression stroke of the The following working chamber of the internal combustion engine already has displacement charger sucked in over 90 ° eccentric shaft rotation angle, and it is now from the piston of the Internal combustion engine released the loading opening again, so that the positive displacement charger can suck through the suction chamber of the internal combustion engine. This joint suction takes place via 180 ° eccentric shaft rotation angle, which is followed by both Machines during the next 180 ° eccentric shaft rotation angle of the compression stroke takes place when the connection line is constantly open. At the end of this 180 ° is the compression stroke of the positive displacement charger and the overflow process ended, and the working area of the positive displacement charger is again to suck in charge through the next one, which is now in the suction cycle Working chamber of the internal combustion engine ready. The proposal according to the invention has the great advantage that the gas exchange of the positive displacement charger does not depend on the positive displacement charger itself is controlled, but by the piston of the internal combustion engine, as the positive displacement charger sucks through the intake working chamber of the internal combustion engine and the pushes compressed charge through the same line into the same working chamber. If you use a rotary piston machine in trochoid design as a positive displacement loader a transmission ratio of 1: 2, which has two work spaces, is because of the suction and pushing out through a pipe for this process only one work space is required, while the other work space is used for other purposes can be. A reciprocating piston loader can of course also be used as a positive displacement loader be used, which can be kept very simple in its design, since he no inlet and outlet valves or other controls are required.

In order to generate the power required by the operation of the loader, a post-expansion machine, e.g. B. an exhaust turbine is provided. The combustion gases are in the internal combustion engine after they have expanded in transferred to the expansion machine, where they continue to expand can. In order not only to the power requirement in the internal combustion engine set according to the invention of the loader, but at the same time it also increases the efficiency of the machine increase, is proposed according to the invention analogously to the arrangement of the positive displacement charger, with the eccentric shaft of the internal combustion engine also an expansion machine of this kind to couple that they have an expansion and a rotation angle of eccentric shaft at 360 ° Exhaust stroke executes and its expansion stroke after the start of the expansion stroke the internal combustion engine begins and ends at the same time with or after this and Your work area only has an extension opening in the area of the off-axis zone of the Expansion chamber of the internal combustion engine is connected by a line. The expansion machine, in turn, does not need its own control, as it is controlled by the same power expanding gases from the expansion chamber of the internal combustion engine receives and the expanded gases through the same line and through the now im Extension stroke located working chamber of the internal combustion engine pushes out. The expansion machine can be a reciprocating engine. However, it is particularly advantageous as well Expansion machine a rotary piston machine of the trochoid type with a transmission ratio of 1: 2 to be used, in turn only one working space for the expansion and Extension cycle is required, while the second work area is used for other purposes is available. The summary is a particular structural simplification the positive displacement supercharger and the expansion machine in a common rotary piston machine with a transmission ratio of 1: 2, one of which is working space only with the loading opening and whose other work space is only permanently connected to the ejection opening.

When using a rotary piston machine in trochoid design with a transmission ratio of 1: 2 as a positive displacement charger or as an expansion machine The working space not required for the pre-compression or post-expansion can be advantageous to convey air into the exhaust line of the internal combustion engine for the purpose of Afterburning can be used by constantly having this work space with a pipe is in communication, which is in an air inlet duct provided with a suction valve and one provided with a pressure valve with the exhaust pipe of the internal combustion engine communicating air outlet duct forks.

The constant connection to the loading opening, to the ejection opening or lines leading to the air inlet and outlet ducts with the two working spaces the 1: 2 rotary piston machine can be achieved in that in both side walls of the housing of the rotary piston machine recesses are provided whose outer contours correspond to the inner envelope of the piston and in each of the one to the loading opening or to the discharge opening or to the air inlet and outlet ducts opens, with one piston flank on the edge facing one side wall and the other piston flank on the edge facing the other side wall Has bevel, such that the one working space always with the one recess and the other work space is always connected to the other recess.

Some embodiments of the invention are given below with reference the drawings explained in more detail. It shows F i g. 1 is a graph of volume changes the rotary piston internal combustion engine and the positive displacement supercharger, based on the angle of rotation the eccentric shaft, F i g. 2 shows a schematic representation of a rotary piston internal combustion engine with reciprocating piston loader, F i g. 3 is a schematic representation of a rotary piston internal combustion engine with rotary piston charger, FIG. 4 shows a section along line 4-4 in FIG. 3, however with schematically drawn, not sectional channels, FIG. 5 is a diagram similar to FIG. 1, the changes in volume of the rotary piston internal combustion engine and of the expansion machine as a function of the eccentric shaft rotation angle shows F i G. 6 is a schematic representation of a rotary piston internal combustion engine, which with a reciprocating supercharger and a reciprocating expansion machine is coupled, and F i g. 7 is a schematic representation of a rotary piston internal combustion engine, which with a rotary piston machine for additional air and post-expansion is coupled.

Let us first refer to FIG. Reference is made to 1, which shows the change in volume of the three working chambers 1, 11 and 111 of the rotary piston internal combustion engine and the change in volume of a working chamber of a displacement charger IV, which executes an intake and a compression stroke at a 360 ° angle of rotation of the eccentric shaft. This loader can be a reciprocating piston loader according to FIG. 2 or a rotary piston charger according to FIG. 3 be.

In the case of a rotary piston internal combustion engine with a double-arched epitrochoid, each work cycle extends over a 270 ° angle of rotation of the eccentric shaft. The phase shift between successive working chambers is 360 °. Correspondingly, in the diagram according to FIG. 1 the suction process for chamber 1 (dashed line) from 0 to 270 °, and compression takes place from 270 to 540 °. The chamber II (dash-dotted line) sucks in from 360 to 630 ° and compresses from 630 to 900 °. The suction process of the chamber 111 begins at 720 °. The change in volume of the positive displacement supercharger, in which the intake stroke and the compression stroke each extend over 180 ° eccentric shaft rotation angle, is shown by line IV. The drive shaft of the positive displacement supercharger is coupled to the eccentric shaft of the internal combustion engine in such a way that the supercharger begins its intake stroke at 90 ° and ends at 270 °. The compression stroke takes place from 270 to 450 ° and then the next intake stroke from 450 to 630 ° and the following compression stroke from 630 to 810 °.

The mode of operation is as follows: Only chamber 1 sucks in during route a. During the distance b, the suction process takes place both in the chamber 1 and in the displacement charger IV. Over the distance c, compression takes place both in chamber 1 and in charger IV and, at the same time, the charge compressed in charger IV is pushed into chamber 1. At the end of route c, ie when the compression stroke of charger IV ends, it is switched off by chamber I, and the charge sucked in by chamber 1 itself and the charge pushed over by charger IV during route c is only transported over distance d in the Chamber I compressed to the required value. Near the end of path d, the fuel is injected, and the expansion in chamber I now takes place over path e and then over path f, which is not fully shown, the exhaust stroke, which is then followed by path a. In parallel, the chamber 1I has sucked alone during the route a '. The suction process takes place both in the chamber 1I and in the charger IV via the path b ', which connects to the path c. During the distance c 'the compression takes place in both machines, and at the same time the overflow process from the loader IV into the chamber 11 takes place. This overflow ends at the end of the section c ', and during the section d' the entire charge is now compressed in the chamber II. In the meantime, the intake cycle has started in working chamber III at 720 ° (ä '). At 820 ° the charger IV also begins to suck in again, and the sequence of operations previously described for chambers I and II is repeated.

The chamber volume of the loader is generally about the chamber volume correspond to the internal combustion engine if only that for the implementation of the Diesel process necessary compression ratio should be achieved. Should with larger Overload are driven, the chamber volume of the loader is correspondingly larger to get voted.

A corresponding to the diagram in FIG. 1 working unit is in Fig. 2 shown. Here, 1 is a rotary piston internal combustion engine known design shown in cross section. The housing shell 2 of this machine has an inner jacket surface 3 in the form of a double-arched epitrochoid. In the side parts of the housing an eccentric shaft 4 is rotatably mounted, the one Has eccentric 5 on which a triangular piston 6 is rotatably arranged. the The speed of the piston 6 has a ratio of 1 to the speed of the eccentric shaft 4: 3. In the housing shell 2 are an inlet channel 7, an injection nozzle 8 and an outlet channel 9 arranged. When the piston 6 rotates in the direction of arrow D, the change Working chambers I, 1I and III their volume, with each full revolution of the Piston 6 in each of these working chambers with a complete four-stroke process corresponding phase shift takes place. In the position of the piston shown 6 is the chamber 1 at the end of the intake stroke, in chamber IH the goes Expansion cycle ahead of you, and the extension cycle takes place in chamber II.

The crankshaft 10 of a reciprocating piston charger 11 is coupled directly to the eccentric shaft 4. The loader 11 has a cylinder 12 in which a reciprocating piston 13 is slidably mounted. The reciprocating piston 13 is connected to the crank pin 15 of the crankshaft 10 by a connecting rod 14. The working chamber 12 ′ is connected to the working chamber 1 via a line 16 and a loading opening 17 in a side wall of the housing of the internal combustion engine 1. The reciprocating piston 13 is at bottom dead center, so it has ended its intake stroke. The suction takes place through the inlet channel 7, the working chamber I, the loading opening 17 and the line 16. The position of the reciprocating piston 13 and piston 6 shown corresponds to the angular position 270 ° in the diagram F i g. 1. As the eccentric shaft 4 continues to rotate, compression takes place simultaneously in chamber I and in working space 12 ' , with compression in supercharger 11 being faster due to the compression stroke that only extends over 180 °. It is therefore pushed over the charge during the compression in the charger 11 through the line 16 and the loading opening 17 into the chamber I. As soon as the reciprocating piston 13 has reached its top dead center, the loading opening 17 is covered by the piston 6 opposite the chamber I, and the compression only takes place in the chamber 1. With further rotation of the shafts 4 and 10, the reciprocating piston 13 goes down again, and the loading opening 17 is opened by the piston 6 for the subsequent working chamber 1I, which is already in the intake stroke, the reciprocating piston 13 in the manner described above via the Inlet channel 7, the chamber 1I, the loading opening 17 and the line 16 sucks (distance b 'in Fig. 1). Chamber I has meanwhile finished its compression cycle, whereupon ignition takes place with the fuel injection and the expansion and extension cycle takes place in the usual way.

In the embodiment according to FIG. 3 is the same rotary piston internal combustion engine as in FIG. 2 is connected to a rotary piston charger 20, which is shown in longitudinal section in FIG. 4 is shown. The housing of the rotary piston charger 20 consists of a jacket 21, the inner surface 22 of which has the shape of a single-arched epitrochoid, and of side parts 23 and 24. The drive shaft 25 is coupled to the eccentric shaft 4 in such a way that it rotates at twice the speed of the eccentric shaft 4. It has an eccentric 26 on which a two-cornered piston 27 is rotatably mounted. The speed of the piston 27 has a ratio of 1: 2 to the speed of the shaft 25. The piston 27 and the housing define two working spaces 28 and 29 which periodically change their volume as the piston 26 rotates. In the side walls 30 and 31 of the side parts 23 and 24 , recesses 32 and 33 are provided, the outer contours of which correspond to the inner envelope curve of the piston 27, which are therefore completely covered by the piston contour. The recess 32 is connected via a channel 34 to the line 16 which opens into the loading opening 17. A constant connection of the working space 28 with the recess 32 takes place in that the flank edge 35 of the piston 27 facing the side wall 30 has a bevel 36. There is no connection between the working space 28 and the recess 33. The positions of the piston 6 and the piston 27 correspond to the angular position 90 ° in FIG. 1. The working chamber I has already started its intake stroke, while the piston 27 is at top dead center with respect to the working space 28 and the working chamber 28 is at the beginning of its intake stroke. After a short rotation of the shafts 4 and 25, the loading opening 17 is released towards the working chamber I, and the working chamber I and the working space 28 suck in together. With further rotation, the working procedure runs as in connection with FIG. 1 and 2.

The working space 29 is in this embodiment to the Promotion of air into the exhaust system 37 of the rotary piston internal combustion engine is used. For this purpose, the working space 29 stands over a corresponding bevel 38 in the flank edge 38a with the recess 33 constantly in connection. From the recess A line 39 extends from 33 and extends into an air inlet duct 40 and an air outlet duct 41 forks. A suction valve 42 is in the air inlet channel 40 and there is a suction valve 42 in the air outlet channel 41 a pressure valve 43 is arranged. In the phase shown, the work area has 29 is its largest volume, so it is at the end of its intake stroke. With further rotation of the piston 27 takes place in the working chamber 29, the compression, whereby the valve 42 is closed and the valve 43 is opened and air into the exhaust system 37 is blown in for the purpose of post-combustion.

If the rotary piston charger 20 is designed as a rotary piston machine, the rotating housing can be connected directly to the eccentric shaft without an intermediate gear 4 can be paired.

In the diagram according to FIG. 1, to which the working methods of the in F i g. 2 and 3 are based, the compression strokes of the internal combustion engine begin and loader at the same time. However, it can be advantageous to adjust the compression rate of the Loader start, for example, 30 ° before the compression stroke of the internal combustion engine to let the pressure in the working chamber of the internal combustion engine during the overflow is lower and the overflow losses are reduced.

As a result of the connection of a charger, the overall efficiency of the machine is deteriorated, it is advisable to carry out a post-expansion to at least to cover the power requirements of the loader. Analogous to the arrangement of the loader should therefore an expansion machine can be coupled to the eccentric shaft of the internal combustion engine, whose expansion space is with the working chamber in the expansion stroke Internal combustion engine during the period in which both machines are expanding an overflow channel is in communication. The expansion stroke of the internal combustion engine should begin before the expansion stroke of the expansion machine begins. The diagram according to FIG. 5 shows the mode of operation of such a unit. This diagram can as a continuation of the diagram of FIG. 1 can be viewed from 540 °. The working chamber I expands during the route e. This route is divided into the routes e1 and e., the gases expanding only in chamber I during the path e1. At 90 ° the expansion space V of the expansion machine is switched on, so that during the route e., both machines expand at the same time. The segment f is also divided into two stretches f1 and f., namely slide during the route f 1 both machines off at the same time, while over the distance f. only the chamber I pushes out. The expansion machine has its extension cycle at the end of the path f 1 stops and increases its volume again by taking expansion gases from the next Chamber II receives. Here, too, it is assumed that the expansion machine is one Working cycle executes over 180 ° eccentric shaft rotation angle. The chamber volume of the Expansion machine should be at least equal to the chamber volume of the loader.

The implementation of such a post-expansion is shown in FIG. 6 shown in an aggregate, which with respect to the charging of the F i g. 2 corresponds. The crankshaft 45 of a reciprocating piston expansion machine 46 is directly coupled to the eccentric shaft 4. A reciprocating piston 48 is arranged in the cylinder 47 of this machine and is connected to the crank pin 50 by the connecting rod 49. The working chamber 47 ′ is connected by a line 51 to an ejection opening 52 which is arranged in a side wall of the housing of the rotary piston internal combustion engine 1. The reciprocating piston 48 is at top dead center, so it has just ended its extension stroke. This place. Jung corresponds in the diagram according to FIG. 5 the angular position 90 °. With further rotation of the shafts 4 and 45 in the direction of rotation D and the resulting downward movement of the piston 48, the ejection opening 52 is released towards the working chamber I, and the expanding gases can also enter the working space 47 'through the ejection opening 52 and the line 51 and there expand. If the reciprocating piston 48 is at bottom dead center, the outlet channel 9 for the chamber I is released, and the common pushing out begins corresponding to the distance f 1 in FIG. 5 until the reciprocating piston 48 is again in the position shown in FIG. 6 is the position shown, in which the expansion machine is ready to receive expansion gases from the subsequent chamber II.

The positive displacement loader and expansion machine can also be used in one machine be united. The rotary piston machine is particularly suitable for this in trochoid design with transmission ratio 1: 2, as this machine has two working chambers of which one for pre-compression and the other for post-expansion can be used. Such an embodiment is shown in FIG. 7 shown. the The construction of the rotary piston machine 20 ′ corresponds completely to the machine 20 in Fig. 3. The part relating to the charging is also in accordance with the execution F i g. 3 identical. But while in FIG. 3 the workspace 29 for the promotion of Air was used in the exhaust line of the internal combustion engine is shown in FIG. 7 this working space 29 'is used as an expansion space. For this purpose the Line 39 'into line 51, which starts from the ejection opening 52. The piston 6 of the rotary piston machine 1 is shown in the same phase position as FIG. 3, however, the working chamber I has just started its extension cycle, is located thus with reference to the diagram F i g. 5 in the angular position 270 °. The work space 29 'also has its largest volume at the moment and begins through the lines 39 'and 51, the ejection opening 52, the working chamber I and the outlet channel 9 to be pushed out. If the piston 6 comes into the position shown in dashed lines, which is shown in FIG. 5 the The angular position corresponds to 450 °, the working space 29 'has ended its extension cycle, and the ejection opening 52 is controlled by the chamber I. After further rotation comes the ejection opening 52 with the chamber II, which is now in the expansion cycle in connection, so that expanding gases in the now again increasing work space 29 'can overflow.

In the diagram F i g. 5 and in the statements according to FIG. 6 and 7 the expansion strokes of the internal combustion engine and the expansion machine end at the same time. Here, too, it can be advantageous to use the two machines so with each other to couple that the expansion stroke of the expansion machine later, for example 30 ° after the end of expansion of the internal combustion engine ends. Accordingly begins the overflow later, which is advantageous because then at the beginning of the overflow the pressure and the temperature in the expansion chamber of the internal combustion engine already is lower, so that the flow losses and the overflow are reduced takes place at a lower temperature.

In all the exemplary embodiments, those with the internal combustion engine were used coupled machines, for the sake of clarity, are axially parallel to one another shown. In practice, the machines are arranged coaxially next to each other, and the overflow ducts are in the partition walls between the individual machines placed in order to keep the overflow paths small and thus the harmful spaces and the flow resistances to keep it low.

Claims (1)

Claims: 1. Internal combustion engine set based on the diesel process works, consisting of an internal-axis rotary piston four-stroke internal combustion engine with a two-arched inner surface and a triangular, rotatable on one Piston arranged on the eccentric shaft, and a displacement charger coupled to this, the internal combustion engine having a loading opening in the area of its compression chamber has, which is connected to the working space of the positive displacement charger via a line is that the positive displacement charger (11 resp. 20, 20 ') is coupled to the eccentric shaft (4) in such a way that it is at a 360 ° angle of rotation of the eccentric shaft performs an intake and a compression stroke and its compression stroke at the same time begins with or shortly before the compression stroke of the internal combustion engine and that his Working space (12 ', 28) is only connected to the loading opening (17) and this Loading opening (17) is arranged in the area of the off-axis zone of the shell (2). z. The internal combustion engine set of claim 1, wherein the internal combustion engine has a Expansion machine is connected, the working chamber burned gases from the internal combustion engine are supplied, characterized in that the expansion machine (46, 20 ') with the eccentric shaft is coupled in such a way. that they are at 360 ° eccentric shaft rotation angle carries out an expansion and an extension cycle and its expansion cycle after the beginning of the expansion stroke of the internal combustion engine begins and simultaneously with or ends after this and its working space (47 ', 29') has only one ejection opening (52) in the area of the off-axis zone of the expansion chamber of the internal combustion engine is in communication by a line (51). 3. Internal combustion engine set according to claim 1 and 2, characterized in that the displacement charger and the expansion machine from a common rotary piston machine (201 in trochoid design with a transmission ratio 1: 2 are formed, one of which is a working space (28) only with the Loading opening (17) and its other working space (29 ') only with the ejection opening (52) is constantly connected. 4. Internal combustion engine set according to claim 1 or 2, characterized characterized in that the positive displacement charger or the expansion machine is a rotary piston machine (20) is trochoidal type with a gear ratio of 1: 2; whose one work space (28) used as a suction and compression space or as an expansion and exhaust thrust space is and the other working space (29) is constantly connected to a line (39) which is located in an air inlet duct (40) provided with a suction valve (42) and one provided with a pressure valve (43); with the exhaust line (37) of the Internal combustion engine related air outlet = channel (41) forks. 5. Internal combustion engine set according to claim 3 or 4, characterized in that in the two side walls (23, 24) of the housing of the rotary piston machine (20 or 20 ') recesses (32, 33) are provided, the outer contours of which correspond to the inner envelope curve of the piston (27) and in each of which a line (34 or 39 or 39 ') opens, and that one piston flank on the edge (35) facing one side wall (23) and the other piston flank a bevel (36) on the edge (38a) facing the other side wall (24) or 38) in such a way that the one working space (28) always has one recess (32) and the other working space (29) are always connected to the other recess (33) is.